EP1642023B1 - Connection for high-pressure spaces of fuel injectors - Google Patents

Abstract

The invention relates to a connection point of a space (4), which is subjected to the action of high pressure, in a highly pressurized body (11) of a high-pressure injection system for fuel to a boring (12) extending through the body (11). This boring extends in an essentially vertical manner inside the body (11). A cylindrically shaped pocket (19) or a peripheral groove (18) is formed in the space (4) subjected to the action of high pressure. The boring (12) leads into said pocket or peripheral groove while forming an intersection point (17).

Description

To introduce fuel into direct-injection internal combustion engines, stroke-controlled injection systems with high-pressure storage space (common rail) as well as pump-nozzle systems or pump-line-nozzle systems are used. In fuel injection systems with high-pressure storage space can be adjusted in an advantageous manner, the injection pressure to load and speed of an internal combustion engine in wide operating ranges. To reduce emissions and achieve high specific power, high injection pressure is required. The achievable pressure level of HochdruckkraftstoiFpumpen is limited for reasons of strength, so that come to further increase the pressure in fuel injection pressure booster in the fuel injectors used.

State of the art

DE 101 52 261 A1 discloses a connection point of a high-pressure accumulator designed as a high-pressure chamber of a high-pressure injection system for motor vehicles. The pressurized space is a high-pressure accumulator in the form of a common rail of a diesel injection system. The high-pressure accumulator is formed by a hollow body, in which opens a transverse bore. To increase the compressive strength is proposed to attach to the outer and / or inner surface of the hollow body one or more notches and / or recesses for stress relief of the pressurized hollow body. The notches and recesses are mounted in the vicinity of the transverse bores or extend in the axial direction close to the transverse bore.

Another high-pressure accumulator in the form of a common rail for a diesel injection system is known from US 6,520,155 B1. In order to withstand higher pressures, the main body of the high-pressure accumulator has at least two connecting openings, which are arranged diametrically opposite one another, so that in the interior the point of confluence of the transverse bore can simply be rounded off in terms of manufacturing technology.

The document DE 199 48 339 C1 also relates to a connection point to a common rail of a diesel injection system, wherein at least two substantially circular-cylindrical recesses are executed in the interior of the base body, so that the transverse bore introduced into the base body into the recess and not in the Cylinder wall of the interior of the high pressure accumulator opens.

Another connection point for a high-pressure line in an injector body of a fuel injector is known from DE 100 22 378 A1. In the injector body, a high-pressure collecting space is formed, into which an inlet bore opens. In this case, a recess in the cylinder wall of the high-pressure accumulation chamber is executed, into which the inlet bore opens.

The document DE 102 18 904 A1 has a fuel injection device for internal combustion engines with a fuel injector, which can be supplied by a high-pressure fuel source, with a pressure intensifier designed as a pressure booster. Between the fuel injector and the high-pressure fuel source, the pressure translation device having a movable pressure booster piston is connected. The pressure booster piston separates a connectable to the high-pressure fuel source space from a high-pressure chamber connected to the fuel injector. By filling a back space (differential pressure chamber) of the pressure booster device with fuel or by emptying the back space of fuel, the fuel pressure in the high-pressure chamber can be varied. The fuel injector has a movable closing piston for opening and closing injection openings. The closing piston protrudes into a closing pressure chamber, so that the closing piston can be acted upon by fuel pressure in order to achieve a force acting on the closing piston in the closing direction. The closing pressure chamber and the rear space are formed by a common closing pressure-return chamber, wherein all portions of the closing pressure-return space are permanently interconnected to exchange fuel. There is provided a pressure space for supplying the injection openings with fuel and for acting on the closing piston with a force acting in the opening direction. A high-pressure chamber communicates with the high-pressure fuel source in such a way that in High pressure chamber, apart from pressure oscillations, constantly at least the fuel pressure of the high-pressure fuel source may be present, wherein the pressure chamber and the high-pressure chamber are formed by a common injection space. All sections of the injection space are permanently connected to each other for the exchange of fuel.

From DE 102 47 903.8 A1 a pressure-reinforced fuel injection device with internal control line can be removed. The fuel injector, which communicates with a high pressure source, has a multi-part injector body. In this one is actuated via a differential pressure chamber actuated pressure intensifier whose pressure booster piston separates a working space of the differential pressure chamber. The fuel injection device can be actuated via a switching valve. A pressure change in the differential pressure chamber of the pressure booster via a central control line which extends through the pressure booster piston. The central control line is guided through the working space of the pressure booster and sealed against this via a high-pressure-tight connection.

DE 196 11 884 A1 relates to a fuel injection valve for internal combustion engines. This comprises a valve member in an axially displaceable piston-shaped valve member. This has at its combustion chamber end a valve sealing surface which cooperates to open up an injection cross-section with a provided on the combustion chamber end of the bore valve seat. Further, this has a pointing in the direction of valve sealing surface pressure shoulder, through which the valve member is divided into a larger diameter in the bore slidably guided guide member and a smaller diameter free shaft portion. It is provided by a cross-sectional widening of the bore formed pressure chamber which is connected via a formed between the free shaft of the valve member and the wall of the bore gap with the valve seat and at the valve seat remote from the end of the guide member of the valve member receiving guide portion of the bore followed. The valve body is traversed by a pressure channel, which opens radially outward of the bore in the valve seat facing away from the end of the pressure chamber. The pressure shoulder on the valve member constantly immersed so far in the guide portion of the bore, that at the pressure chamber adjacent the end of the guide portion of the bore an annular gap between the valve member and the wall of the bore remains. In this a counterforce is built up on a remaining between the bore and the pressure channel web.

In previous embodiments of pressure amplifiers controlled via the differential pressure chamber, the differential pressure chamber is connected by a generally horizontal bore to a second valve-carrying bore. The production of horizontal drilling turns out to be extremely difficult. Time-consuming and expensive processes such as electrochemical sinking or erosion must be used here. In addition, occur at the Verschneidungsstellen between the back space and the horizontal bore the highest stresses in the component. A higher surface quality and a rounding of production-related resulting edges are no longer sufficient for the desired still to be increased system pressures to obtain durable components. The known from DE 102 47 903 A1 inside central control line requires a higher manufacturing and assembly costs than simple holes within the injector.

Presentation of the invention

In the design of pressure amplifiers controlled via the differential pressure chamber, the connection of the differential pressure chamber to the control line constitutes a potential weak point. Since the control valve for operating the pressure intensifier is arranged above the pressure intensifier for reasons of space, the control line is guided laterally past the pressure intensifier. After the proposed solution according to the invention, the connection between the differential pressure chamber (back space) and the control line, which is usually designed as a bore and leads to the valve, represented by a circumferential groove or a side pocket in the cylindrical rear space of the booster. The resulting advantage is that especially at the Hockdruckverschneidungsstelle between differential pressure chamber (back space) and a groove or between the differential pressure chamber (back space) and the cylindrically shaped pocket no voltage increases, which affect the pressure resistance of the fuel injector. At the Hochdruckverschneidungsstelle between the groove and formed as a bore control line or the cylindrical shaped pocket and formed as a bore control line, the voltage overshoot can be significantly reduced, so that realize with such a fuel injector with optimized connection between the high-pressure chambers at the pressure booster higher injection pressures to let.

Another advantage of the proposed solution according to the invention is to be seen in that a tolerance insensitive Verschneidungsstelle between the groove or the pocket and the bore formed as a control line is achieved, since purely mechanical, machining production method for producing the groove or pocket can be used.

By appropriate shaping of the groove or the cylindrically shaped pocket specific shapes of the breakthrough can be realized, for example in an oval rectangular or other geometry. Leave through a defined form of breakthrough the voltages in the area of the high-pressure intersection point between the groove and the control line designed as a bore or between the cylindrically shaped pocket and the control line designed as a bore can be specifically influenced and further reduced further. With such trained connection points in the high pressure area between high-pressure chambers of components that are exposed to high pressures, can be seen on the one hand in the long run, reduce the life of fuel injectors with pressure boosters due to the lower voltage levels, on the other hand, by the invention proposed connection of high-pressure chambers of the highest pressure components further increase of the injection pressure level in fuel injectors possible.

drawing

With reference to the drawing, the invention will be described below in more detail.

Figur 1

einen über Druckvariationen in einem Differenzdruckraum aktivierten Druck-verstärker im nicht aktivierten Zustand,

Figur 2

den Druckverstärker gemäß Figur 1 im aktivierten Zustand,

Figur 3

einen Druckverstärker im Halbschnitt, dessen Differenzdruckraum (Rückraum) mittels einer Horizontalbohrung mit einer als Bohrung beschaffenen Steuerleitung in Verbindung steht,

Figur 4

eine erfindungsgemäß konfigurierte Anbindung eines Rückraumes im Körper des Druckverstärkers mit einer als Bohrung ausgebildeten Steuerleitung, ebenfalls im Halbschnitt,

Figur 5

eine abgewickelte Begrenzungswandung eines Druckraumes, in welchem eine zylindrisch geformte Tasche ausgebildet ist, die mit einer als Bohrung ausgebildeten Steuerleitung eine Anbindung bildet,

Figur 6

eine abgewickelte Begrenzungswandung eines Hochdruckbehälters, in welchem eine ebenfalls abgewickelt dargestellte Umlaufnut eingebracht ist, die ebenfalls mit einer als Bohrung beschaffenen Steuerleitung in Verbindung steht,

Figur 7.1

eine Anbindung eines Differenzdruckraumes eines Druckverstärkers mit einer als Bohrung beschaffenen Steuerleitung,

Figur 7.2

eine erfindungsgemäß konfigurierte Anbindung einer als Bohrung beschaffenen Steuerleitung mit dem Differenzdruckraum (Rückraum) eines Druckverstärkers und

Figur 7.3

eine als Umlaufnut ausgebildete Anbindung eines Differenzdruckraumes (Rückraum) eines Druckverstärkers mit einer als Bohrung beschaffenen Steuerleitung.

It shows:

FIG. 1

a pressure amplifier activated via pressure variations in a differential pressure chamber in the non-activated state,

FIG. 2

the pressure booster according to FIG. 1 in the activated state,

FIG. 3

a pressure amplifier in half section whose differential pressure chamber (back space) is connected by means of a horizontal bore with a control line designed as a bore,

FIG. 4

an inventively configured connection of a back space in the body of the pressure booster with a bore formed as a control line, also in half section,

FIG. 5

a developed boundary wall of a pressure chamber, in which a cylindrically shaped pocket is formed, which forms a connection with a bore formed as a control line,

FIG. 6

a developed boundary wall of a high-pressure container, in which a circulation groove also shown unwound is introduced, which is likewise connected to a control line designed as a bore,

Figure 7.1

a connection of a differential pressure chamber of a pressure booster with a control line designed as a bore,

Figure 7.2

an inventively configured connection of a bore designed as a control line with the differential pressure chamber (back space) of a pressure booster and

Figure 7.3

designed as a circulation groove connection of a differential pressure chamber (back space) of a pressure booster with a designed as a bore control line.

variants

1 is a schematic illustration of a pressure booster whose working space is separated from a pressure-relieving or pressurizable differential pressure chamber via a booster piston.

Furthermore, the pressure booster 1 comprises a compression chamber 5 formed in its body 11. The booster piston 3 separating the differential pressure chamber 4 (back space) from the working space 2 comprises a first end face 6 and a first end face 6 The compression chamber 5 limiting the second end face 7. About a high-pressure source, not shown in Fig. 1, the working space 2 of the pressure booster 1 with system pressure (P _rail ) is applied. In the differential pressure chamber 4, the system pressure (p _rail ) also prevails in the compression chamber 5 of the pressure booster 1, which is shown in its deactivated position 8 in FIG. 1, the system pressure level p _rail also prevails. The pressure booster 1 is therefore pressure-balanced, since the pressure forces acting on the second end face 7 and the annular surface in the differential pressure arm 4 of the pressure amplifier 1 correspond to the pressure force acting on the first end face 6 of the booster piston 3.

FIG. 2 shows a pressure amplifier according to the representation in FIG. 1 in its activated state.

By way of a pressure relief of the differential pressure _chamber 4 to a pressure level p _{fuel, recum} , the booster _piston 3 moves into the compression space due to the pressure force acting on its first end face 6 in the working space 2, which is generated by the system pressure (p _rail ) 5 on. The second end face 7, which delimits the compression space 5 of the pressure booster 1, compresses the fuel supply contained in the compression space 5 to an elevated pressure level (p _amplified ) which can be achieved in the direction of an inlet 10 to one in FIG. 2, in accordance with the design ratio of the pressure booster piston 3 directed injection valve member is passed.

Figure 3 shows a half section through a body of a pressure intensifier according to the prior art.

The pressure booster 1 comprises a body 11 in which a control line 12 designed as a bore runs. Trained as a bore control line 12 is connected via a horizontal bore 13 with the differential pressure chamber 4 (back space) of the booster 1 in combination. Within the critical region 14, also referred to as intersection region, a first Verschneidungsstelle 15 forms with the bore formed as a control line 12 and the horizontal bore 13 and a second critical Verschneidungsstelle 16 between the horizontal bore 13 and the rear space 4 of the booster 1 from. At these points of intersection 15 and 16, the highest voltages occur during operation of the pressure booster 1, which affect the continuous operating stability of such a pressure booster 1 with horizontal bore 13 crucial. In a half section through the body 11 of the pressure intensifier 1 as shown in Figure 3, the compression chamber 5 is shown, branches off from the under an adjusting depending on the design of the booster 1 angle of the inlet 10 to an injection valve member, not shown in Fig. 3.

4 shows an embodiment according to the invention of a connection between the control line 12 designed as a bore and a differential pressure chamber (back space) of a pressure booster.

From the illustration according to FIG. 4, it can be seen that a circulation groove 18 can be formed at the lower end of the differential pressure chamber 4 of the pressure intensifier 1 or a cylindrically shaped pocket 19. At a first bore intersection 17 between the circumferential groove 18 and the first proposed bore according to the invention. the cylindrically shaped pocket 19 adjusts itself to a first bore intersection 17, while a second bore intersection 22 is formed between the differential pressure space 4 (rear space) of the pressure booster 1 and the cylindrically shaped pocket 19 or the circumferential groove 18. The differential pressure chamber 4 is limited at its lower end by an annular surface 20; in half section of FIG. 4 is shown at the lower end of the body 11 of the booster 1 of the compression chamber 5, from the lower an angle of inclination of the inlet 10 branches off to the injection valve member, not shown in Fig. 4.

The illustration according to FIG. 5 shows a boundary wall of a high-pressure container with a cylindrically shaped pocket shown in an extended position of 180 °.

In the illustration according to FIG. 5, the boundary wall of the differential pressure chamber 4 (rear space) of a pressure booster in a 180 ° stretched position is shown. The tangential stresses in the body 11 of the pressure intensifier 1 caused by the internal pressure in the differential pressure chamber 4 (back space) act in the unwound cuboid as shown in FIG. 5 as tensile stresses represented by the two arrows pointing away from each other. In the area in which two bores would meet, the notch effects occurring at the point of intersection 15 according to FIG. 3 are added along bores 12 and 13, and consequently a clear increase in stress occurs. In the illustration according to FIG. 5, the connection of the control line 12 designed as a bore to the differential pressure chamber 4 (rear space) is designed as a cylindrically shaped pocket 19 which exhibits no notch effect. Compared to the connection of the differential pressure chamber 4 to the formed as a bore control line 12 of FIG. 3 by means of a horizontal bore 13 results from the invention shown in Fig. 5 Forming the connection only a notch action point 23 along the bore 12, at which compared to Both results in accordance with FIG. 3 notch action points 15 and 16, sets a significantly lower voltage level.

In the illustration according to FIG. 6, the connection of the differential pressure chamber to a control line designed as a bore is represented by means of a circumferential groove.

According to the embodiment shown in Fig. 6 a connection of the differential pressure chamber to a bore formed as a control line 12 is shown in unwound 21 position wall of a high-pressure chamber such as a differential pressure chamber 4 of a pressure booster 1 also shown in a stretched circumferential groove 18. The circumferential groove 18 is not kerbwirkungsfrei, along the bore 12 forms the notch action point 23, which represents the location at which the maximum stresses 24 occur. Also in the illustration according to Fig. 6, those in the component, i. Tangential voltages occurring in the body 11 in the unwound layer 21 of the body 11 are shown as Zuspannungen.

In the two variants shown in FIGS. 5 and 6, a connection of a high-pressure-carrying space to a control line 12 formed as a bore, which in FIG the body 11 is perpendicular, only one notch action point 23 is formed in each case. Meet at the Verschneidungsstelle 15 of the horizontal bore 13 as shown in FIG. 3 with the formed as a bore control line 12 the notch effects along the bores 12 and 13, so that add according to the known from the prior art embodiments shown in Fig. 3, the notch effects and lead to a significant voltage increase in the component 11.

In contrast, although a circumferential groove 18 in FIG. 6 weakens the overall cross-section of the body 11 somewhat, the circumferential groove 18 does not act like a notch under tensile load with respect to the resulting mechanical load. As a result, a voltage increase at the notch action point 23 is avoided, so that only one notch action point 23 is formed, which represents the location 24 at which the maximum stresses occur. Compared to the embodiment according to FIG. 3 with the embodiment of the connection as a horizontal bore 13, however, a considerably lower stress level arises at the notch action point 23. If the connection between the control line formed as a bore 12 and a high-pressure container, however, designed as a cylindrically shaped pocket 19, this embodiment of the connection offers the advantage that the cylindrically shaped pocket 19 causes a smaller dead volume compared to a circumferential groove 18, i. the high-pressure vessel when forming the connection as a cylindrically shaped pocket 19 can be filled with a smaller volume. If the dead volume can be reduced, for example, in the differential pressure chamber 4 of the pressure booster 1, this advantageously leads to an increase in the efficiency; Furthermore, the hydraulic tuning can be improved and last but not least - in the case of a booster - smaller Absteuermengen be moved when activating the booster.

Fig. 7.1 is a connection of a differential pressure chamber to a bore formed as a control line by means of a horizontal bore removed.

The differential pressure chamber 4 is constructed symmetrically to an axis of symmetry 25. The control line 12 and the differential pressure chamber 4 are connected to each other via the horizontal bore 13, so that the first Verschneidungsstelle 15 between the horizontal bore 13 and the control line 12 results, and the second Verschneidungsstelle 16 through the horizontal bore 13 and the differential pressure chamber 4 (rear space) is shown , The notch effects formed at the Verschneidungsstelle 15 add up, so that sets a first, very high voltage level σ _{max, 1} during operation of the pressure booster.

In the illustration according to FIG. 7.2, the connection of the differential pressure chamber (rear space) to the control line designed as a bore is formed by a cylindrically shaped pocket.

The cylindrically shaped pocket 19 is formed in the lower region of the differential pressure chamber 4 in its inner wall. The cylindrically shaped pocket 19 forms the attachment point between the control line 12 formed as a bore and the differential pressure chamber 4 (rear space) in the body 11. The control line 12 can be designed both as a blind bore (FIG. 7.1) and as a through bore 12.1. Due to the shape of the attachment point as a cylindrically shaped pocket 19, a first bore intersection 17 sets in which represents the notch action point 23. In comparison to the illustration according to FIG. 7.1, only one notch effect contribution through the bore intersection 17 is shown. This stress concentration point 23 represents the location 24 represents, at which a maximum stress σ _{max, 2} occurs, which significantly added under the occurring in Fig. 7.1 maximum stress σ _{max, 1.} As a result, during operation of a high-pressure container, such as a differential pressure chamber 4 of a pressure booster, the stress level occurring in the body 11 thereof can be reduced by up to 30%. The cylindrically shaped pocket 19 is formed in the lower portion of the inner wall of the differential pressure chamber 4 (back space) in the body 11 and also provides only a small increase in the dead volume within the differential pressure chamber 4. The maximum height of the cylindrically shaped pocket 19 is identified by reference numeral 30; the cylindrically shaped pocket 19 extends symmetrically semicircular and runs in outlet areas 31 in the inner wall of the differential pressure chamber 4 (rear space). The notch effect occurring at the second bore intersection 22 between the cylindrically shaped pocket 19 and the wall of the differential pressure chamber 4 is negligible compared to the stress exaggeration caused by the notch effect at the first bore intersection 17.

Fig. 7.3 shows the impact variant in cross section, in which the connection of the bore formed as a control line to the differential pressure chamber via a circumferential groove in the pressurized body.

According to this embodiment variant, the circumferential groove 18, which is formed at a constant height 32, forms a first bore intersection 17. The first hole intersection 17 marks the transition point of the bore 12 formed as a control line to the circumferential groove 18; Furthermore, a second bore intersection 22 sets in which represents the transitional area between the differential pressure chamber 4 (rear space) and the circumferential groove 18. The lower annular surface of the circumferential groove 18 is identified by reference numeral 20. To the circumferential groove 18 more holes 33 may be connected, one of which is shown in Fig. 7.3. The intersection 17 between the control line 12 designed as a bore and the circumferential groove 18 represents the notch action point 23, which represents the location 24 of the maximum stress σ _{max, 3} . Compared to the maximum stress σ _max, 2 occurring in the embodiment according to FIG. 2, the maximum stress σ _{max, 3} occurring in the embodiment according to FIG. 7.3 is again reduced.

The contour of the circumferential groove 18 and the cylindrically shaped pocket 19 may be arcuate, angular, formed with rounded corners or in other geometry.

The embodiments shown in FIGS. 5, 6 and 7.2 and 7.3 of connection sites between high-pressure-carrying spaces and a bore extending essentially vertically through a body avoid sharp-edged transitions and thus permit a reduction of the occurring stress level. The reduction of the maximum voltage occurring in the body 11 due to tangential stress when pressurizing the differential pressure chamber 4 (back space), for example, a pressure booster 1 allows on the one hand a further increase in the pressure level within the body 11, on the other hand, while maintaining the currently prevailing pressure levels, an extension of the service life of a pressurized body 11th ,

LIST OF REFERENCE NUMBERS

1

booster

2

working space

3

intensifier piston

4

Differential pressure chamber (backspace)

5

compression chamber

6

first end face

7

second end face

8th

deactivated position

9

activated position

10

Inlet to injection valve member

p _rail

System pressure level

p _amplified

increased pressure level

p _{fuel, return}

Druckniveauabsteuerung

11

high-pressure body

12

Control line (hole)

12.1

Control line (hole)

13

horizontal drilling

14

intersection

15

first point of intersection

16

second point of intersection

17

first bore intersection
(Control cable with pocket / groove)

18

circumferential groove

19

cylindrically shaped bag

20

ring surface

21

unwound wall high-pressure vessel (180 ° extension)

22

second bore intersection (differential pressure chamber with pocket / groove)

23

Notch effect point

24

Place of maximum tension

25

axis of symmetry

26

Intersection control line / Hori zontalbohrung

27

Intersection control line / bag

28

Intersection of the control line / order

29

pocket geometry

30

Maximum height bag

31

Spout area pocket

32

Height of circumferential groove

33

further drilling

σ _{max, 1}

Maximum voltage for connection according to the prior art

σ _{max, 2}

first reduced maximum voltage level

σ _{max, 3}

further reduced maximum voltage level

Claims (9)

1. Tie-up point of a high-pressure-loaded differential-pressure space (4) of a pressure intensifier (1) in a high-pressure-loaded body (11) of a high-pressure injection system for fuel to a control line (12) which extends through the body (11) and is led laterally past the pressure intensifier, the control line (12) leading to a valve actuating the pressure intensifier (1), characterized in that the differential-pressure space (4) has formed in it a cylindrically shaped pocket (19) or peripheral groove (18), into which the control line (12) issues so as to form an intersection point (17).
2. Tie-up point according to Claim 1, characterized in that the cylindrically shaped pocket (19) or the peripheral groove (18) is arranged in the bottom region of the high-pressure-loaded differential-pressure space (4).
3. Tie-up point according to Claim 1, characterized in that the peripheral groove (18) is formed with an arcuate or angular contour at a constant depth (32) in the body (11).
4. Tie-up point according to Claim 1, characterized in that the cylindrically shaped pocket (19) is designed semicircularly, arcuately or angularly in the body (11) in the wall delimiting the high-pressure-loaded differential-pressure space (4).
5. Tie-up point according to Claim 4, characterized in that the cylindrically shaped pocket (19) has its maximum depth (30) at the point of issue of the control line (12).
6. Tie-up point according to Claim 4, characterized in that the cylindrically shaped pocket (19) has symmetrical run-out regions (31) on both sides of the point of issue of the control line (12) into the said pocket.
7. Tie-up point according to Claim 1, characterized in that the intersection point (17) is designed as a perforation of oval or rectangular geometry, depending on the groove form.
8. Tie-up point according to Claim 1, characterized in that the control line (12) is designed as a throughbore (12.1) in the high-pressure-loaded body (11).
9. Tie-up point according to Claim 1, characterized in that at least one further bore (33) is tied up to the peripheral groove (18) in the high-pressure-loaded body (11).

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